Balanced rotary internal combustion engine or cycling volume machine

ABSTRACT

Balanced rotary cycling machine suitable for use as an internal combustion engine, compressed gas or steam engine, compressor or pump as well as jet propulsion engine is disclosed herein. The rotor assembly consists of four articulating pistons where the opposite pistons are linked with each other by pivoted rods comprising together a parallelogram mechanism and therefore eliminating a need for pivots between pistons. The rotor assembly is rotating inside or outside of circular or non-circular stator depending on the configuration chosen. Variety of apparatuses for variation of the shape of four piston assembly during its rotating cycle are also disclosed herein as well as detailed descriptions of preferred embodiments, including a four cycle internal combustion engine with circular stator, boat engine with polymer parts and four cycle automobile rotary engine with oil pan. In addition, a method of operation of external rotary combustion engine employing a high pressure compressor and an external combustion chamber is disclosed. The invention also teaches a novel lubrication system for rotary automobile engine providing low emissions. The engine has few moving parts, simplified circular or semicircular stator shape and utilizes simple and effective sealing techniques similar to ones employed in Wankel type engines. It is fully balanced, has few moving parts, has very low friction and heat losses due to elimination of pivots at the end of the pistons and employment of optimal configuration combustion chamber with lower area of the surfaces exposed to hot gases.

BACKGROUND OF THE INVENTION

[0001] This invention relates in general to rotary internal combustionengines and more specifically to engines utilizing variable shape rotorknown from the earliest prior art as Werner (U.S. Pat. No. 716,970) typeand opposite to the Wankel type rotary engines with fixed shape rotorand epitrochoidal shape stator. The device also relates to compressors,pumps, vacuum machines, steam or compressed gas engines and othercycling machines.

[0002] In present invention, during the rotation cycle, the rotorpivoting blades or pistons align alternatively in a lozenge and a squareconfiguration so that the volume between the blades itself, side wallsand the stator is changing which allows to create a cycling machine.

[0003] Rotary engines and cycling machines based on the principle ofEdward H. Werner's invention (FIG. 9) of 1902 (U.S. Pat. No. 716,970)and further inventions developed in greater details (FIG. 7) by AlfredJordan (U.S. Pat. Nos. 3,295,505; 3,369,529; 4,181,481) as well as othercycling machines with variable shape rotors are well known from theprior art.

[0004] According to the German Pat. No. 1,295,569 a rotary internalcombustion engine is known, in which two pistons are provided, which areconnected to the shaft by means of two diametrically opposite armsfixedly connected to the shaft.

[0005] Most recent realization of such cycling machine utilizingWerner's principle and described in U.S. Pat. No. 6,164,263 (FIG. 8)employs roll carriages pivotally connected to the ends of the blades andtherefore creating a lateral support for the rotor and simultaneouslyproviding a cam surface for the rotor shape deformation. In this devicean additional variation of the volume between the blades, side coversand a stator is achievable due to variation in relative position of thecarriages and blades.

[0006] Similar configuration indeed is well known from the prior artincluding U.S. patents by Jordan, Ishida and Niemland. These deviceshowever do not employ rolls at the end of sealing carriages except as inthe U.S. Pat. No. 3,387,596 by Niemand where rolls are used incombination with cam surface for deformation of the shape of four linkblades' parallelogram. This cam though was not part of the combustionchamber which provided improved reliability of the device compared toU.S. Pat. No. 6,164,263.

[0007] Parallelogram mechanisms for creating reciprocating movement ofthe pistons are known from the U.S. Pat. No. 5,203,295 by Alexander.Multiple application of unique properties of the parallelogram mechanismare also known, for instance from PCT WO 09105990 A1 by Okulov. Howeverthe common disadvantage exists that the pivoting blades or linksarranged in such configuration are extremely difficult to seal at thepivoting ends.

[0008] Different sealing techniques and methods are described in detailsin the U.S. Pat. Nos. 3,950,017; 3,690,791; 3,918,41; 4,296,936, etc.Particularly, several different types of seals are needed to provideadequate sealing of the device similar to U.S. Pat. No. 6,164,263 whichgreatly complicates design and makes it unreliable. In addition, thecomplicated shape of the parts and greater surface area of combustionchamber both determine high thermal losses and lower efficiency for thistype of engines. Eliminating roll carriages in order to create simplershape for the combustion chamber (or considering its size near zero)brings such design back to the devices like ones described in a U.S.Pat. No. 3,918,415.

[0009] The geometry and numerous configurations of the rotor and statorshapes were detailed in U.S. Pat. Nos. 3,950,117 and 5,288,217 fordifferent types of variable shape rotors. The shape employed in the U.S.Pat. No. 6,164,263 is generally described in prior art and employing nondeformable rotor (FIG. 10) having one to four pivoted carriages runningin a stator of square or other polygon like with rounded corners shape.

[0010] All these engines have an advantage of being near vibrations freecontrary to the Wankel and other type of engines with fixed shape rotoror unbalanced pistons. Disadvantages of the engines however exists thatseals at the pivoting ends of the blades are complicated and there arestill high friction losses due to the significant stress produced by gaspressure and complex shape of the seals and joints.

[0011] In addition the rolls of the carriages being part of thecombustion chamber are exposed to high temperature combustion gases andare suffering deposition of residue products or plaque from thecombustion process. Very complicated configuration of the combustionchamber creates excessive heat transfer to its parts due to largesurface area predetermined by the geometry of the pistons (blades.) Dueto the higher surface area of the combustion chamber/s relatively to itsvolume/s, there is more residue from the non burnt film of the fuel onit. As in most rotary engines, due to centrifugal action of the rotatingrotor forcing the lubricator oil to enter the exhaust, a tendency ofhaving higher overall engine emissions still exists.

[0012] There are also well known devices (so-called “cat and mouse” orscissors type engines) realized in a variety of configurations andutilizing principle of creating cycling volumes between rotating insidethe circular or toroidal housing pistons or blades. The disadvantage ofthese engines is a necessity for creating an external mechanism forvariation of the relative position of the pistons. These devices includecams, oval gears, rotating links mechanisms (Rice), etc. Another knowntype of balanced rotary engines are devices employing cylinders andpistons arranged in a circle and having an activating pistons movementcam with rotating shaft.

[0013] Other engines are represented by concepts proposed in a prior artand including a pressure energy converter, rotary engine or compressoras in U.S. Pat. Nos. 4,068,985, 3,996,899; a rotary disk engine as inthe U.S. Pat. No. 5,404,850; a rotary planetary motion engine as in U.S.Pat. No. 5,399,078; a rotary detonation engine as in the U.S. Pat.4,741,154; a rotary combustion engine as in DE patent 2,448,828, U.S.Pat. Nos. 3,933,131, 4,548,171, 5,036,809; the Wankel type engine as inthe U.S. Pat. Nos. 3,228,183, 4,308,002, 5,305,721, and a continuouscombustion engine as in the U.S. Pat. No. 3,996,899. Most rotaryengines, and particularly the Wankel and those described in the U.S.Pat. Nos. 3,442,257, 3,614,277, 4,144,866, 4,434,757, DE Patent No.3,027,208 are based on the principle of volume variation between a curveand a moving cord of fixed length as a single sliding piston and havethe common disadvantage of not being balanced.

SUMMARY OF THE INVENTION

[0014] The objective of present invention is to provide an engine orfully balanced cycling volume machine with variable shape rotor and lowinternal friction. It is also an objective to provide a rotor enginewith reduced negative effect of the centrifugal forces on the oil orlubricant distribution and utilize a conventional oil pan (pool) designsolution proved to be superior to other types of lubrication systems,particularly the ones used in conventional automobile engines. Stillanother objective of present invention is to create an effective andsimplified engine sealing system.

[0015] It is another object to create possibility of using a simplecircular shape stator and an efficient combustion chamber. Anotherobjects are to create a system for direct and linear transmission ofmechanical torque from all four pistons to the shaft, remove roll camsand pivoting parts from the action of combustion gases, reduce the weighof the engine and provide cleaner exhaust. Still another object is toprovide engine configuration capable of creating a jet propulsory systemand creating an engine for water crafts employing polymer plastic orcomposite parts cooled directly in the water.

[0016] Another object of this invention is to provide a lower rpmengine, utilizing more efficient and less NOx producing (asymmetric)pressure cycle. i.e. giving less time to the compression and exhauststrokes, and allowing more time to the combustion stroke. Another objectof this invention is to provide lower dead time, and to provide anengine tolerant to different fuels as well suitable for photo-detonationmode and hydrogen combustion.

[0017] Alternatively another objective is to create an ignition deviceamplifying the internal pressure during compression cycle to the pointof ignition of air-fuel mixture and to provide an external combustionengine utilizing compressor and expansion machines as per presentinvention.

[0018] The rotor as per present invention comprises of an assembly offour pistons or blades suitable for creation of variable volumes duringits rotation cycle and having sealed gaps between themselves and an ovalor circular shape stator, where the opposite pistons are pivotallylinked to each other creating parallelogram mechanism and where (inbasic configuration) the crossings of said links are connected to therotor shape deforming mechanism and are also coupled with the outputshaft.

[0019] The pistons can have individual seals with stator and side coverscreating variable volume chambers or have seals between them, preferablyat the centers of their relative rotation. The variable chambers can becomposed as shown in the drawings and diagrams below. Intake ports,spark plug and exhaust ports are provided either radial in the statorhousing, or axial in the side covers, or both.

[0020] Different sealing techniques are further presented where sealingbetween pistons and side walls of the stator generally constitute simplelinear or curved semicircular spring loaded seals similar to the Wankeltype engine seals. Apex seals are arranged either between pistons, orbetween pistons and stator contour circular or oval wall, or comprisingadditional seals supported in the mid angle between adjacent pistons andhaving apex seals with them. Another type of continuos seal when used incombination with toroidal shape stator are also disclosed as well asseals employing rollers and supporting roll bearings at the ends of thepistons.

[0021] Rotation of the rotor provides the pistons of the variable rotorto generate cycling volumes thus enabling to provide compression,expansion or vacuum. The engine with four pivoting pistons would havefour strokes cycle firing four times per every revolution, withvirtually no dead time.

BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The following drawings illustrate specific details of presentinvention.

[0023]FIGS. 1, 2, 3, 5, 6, 13 show one preferred embodiment employingfour segmental pistons arranged in lozenge configuration.

[0024]FIGS. 4, 12, 14 illustrate the same embodiment with pistonsarranged in a square configuration.

[0025] FIGS. 7-10 illustrate prior art.

[0026]FIG. 11 is a cross section of the engine from FIG. 12.

[0027]FIG. 12 shows plan view of the preferred embodiment with part ofthe engine side cover not shown.

[0028]FIG. 15 details the extreme positions of the links between pistonsrelative to the piston during engine operation, and FIG. 16 provides across section of the piston side wall in assembly with its side wall.

[0029]FIGS. 17, 23, 27 illustrate engine configuration with lubricatingoil pan (pool) and pistons aligned in a square configuration andsurrounding the stator.

[0030]FIGS. 22, 26, 29 show the same engine with pistons arranged in asquare configuration.

[0031]FIG. 18 is a cross section of the engine as per FIG. 17.

[0032]FIG. 24 is a cross section of the engine as per FIG. 23.

[0033]FIG. 28 is a cross section of the engine as per FIG. 27.

[0034] FIGS. 19-21 illustrate details of the sealing with side sealspositioned in side covers and “apex” seals at the edges of the bed.

[0035]FIG. 25 shows kinematic scheme of the engine as per FIG. 23.

[0036]FIG. 30 details geometry of the cycling machine with “oval” shapestator.

[0037]FIGS. 31 and 32 illustrate pistons with supporting wheels (rolls)positioned in the central part of pistons.

[0038]FIG. 33 illustrates the geometry of the circular stator shape and“ideal” segmental pistons.

[0039]FIGS. 34 and 35 provide the geometry of segmental outer portion ofthe piston creating minimum volume between pistons and a contour wall.

[0040]FIG. 36 illustrates method of determining of the geometrical shapeof the contour wall of “oval” shape.

[0041]FIG. 37 illustrates variations of possible shapes of “oval”contour wall.

[0042] FIGS. 38-40 provide illustration to the method of findingmathematical solution for the definition of contour wall curve.

[0043]FIG. 41, 42 provide diagrams of minimum and maximum volume ofchambers for “oval” type contour wall.

[0044]FIGS. 43, 44 provide diagrams of minimum and maximum volume ofchambers for circular type contour wall.

[0045] FIGS. 45-55 show a variety of rotor and stator configurationsdetermining the shape of the cycling volume chambers.

[0046] FIGS. 56-63 describe principles of determination of engineinternal loads and torque.

[0047] FIGS. 64-75 show a variety of cam mechanisms for piston rotorassembly shape deformation.

[0048] FIGS. 76-83 illustrate different types of supports for pistonscapable of direct receipt of loads from variation of chamber pressures.

[0049] FIGS. 84-89 present different systems for mechanical transfer ofthe torque to the output shaft, where FIGS. 84 and 85 describe prior artand illustrate its disadvantages.

[0050] FIGS. 90-96 are other illustrations of the methods of deformationof piston assembly utilizing oval gears coupled with oval rolls, and thedevices with crank shafts.

[0051] FIGS. 97-107 show a variety of possible pivoted links betweenpistons.

[0052] FIGS. 108-111 are demonstrating details of variation or cyclingof internal volume between pistons.

[0053] FIGS. 112-117 present in greater details engines or compressorswith pistons surrounding the stator or rotor, particularly FIG. 114illustrate a piston or a chain of pistons surrounding a “wavy” stator orrotor and FIGS. 116-117 present the variant of engine with blades orfins associated directly with pistons.

[0054] FIGS. 118-157 illustrate in great details different types ofseals, sealing methods and embodiments.

[0055] FIGS. 158-159 show a variant of the device with circulardeformable contour wall of flexible liner of the stator.

[0056]FIGS. 160 and 161 illustrate rotary engine with “oval” shape rotorand stationary piston assembly.

[0057] FIGS. 162-164 further show the cycling sequence of such device.

[0058] FIGS. 165-166 describe principle of external combustion engine asper present invention,

[0059]FIG. 167 describes an amplified compression type ignition plug andmethod of amplified pressure ignition.

[0060]FIG. 168 present a bottom view of the plug showing slots for gaspassage, and

[0061]FIG. 169 provides explanation to method of amplification ofpressure inside ignition chamber of the plug by means of differentialpiston presented in the FIG. 170.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

[0062] Preferred embodiment comprises a four pistons (each generally ofthe in a form of a disk segment) variable shape assembly where pistonsare linked to each other creating a parallelogram mechanism by means ofat least four pivoted links. The pistons are movably mounted inside theengine housing comprising side walls and a stator of generally circularor semicircular inner profile thus providing a contour wall. (This shapecan also be achieved by using rigid or flexible (deformable) cylindricalliner, which in addition can be deformed to match its configuration tothe ideal geometry of movement of the pistons and apex seals.)

[0063] The shape of the rotor assembly is alternatively changing fromlozenge to square with the help of the piston assembly deformationmechanisms which can be for instance a cam mechanism having roll/s withits axes corresponding to the intersections of the pistons links androcking against the “oval” shape or generally speaking aboutnon-circular orbit.

[0064] Diagrams of operation of the cycling volume machine as a fourcycle internal combustion engine are further presented in the drawings.It is important to mention that the engine can operate as a two cycleengine where two intake ports and two exhaust ports can be provided.Alternatively the inner cycling volume of the engine (between pistons)or external blower also can be utilized for fuel mixture compression ordistribution or as part of the lubrication system, cooling, porting,etc.

[0065] A distinct advantage of the engine as per present invention isthe fact that piston assembly deformation mechanism is actually not apart of the contour wall or stator or rotor configuration which makes iteasy to adjust its properties to different types of fuels, desiredcompression ratios and ratios between the combustion/intake/expansionchambers volumes and angles of the rotor assembly rotation, thusproviding greater flexibility to the design of the device and providingreduction of its cost.

[0066] Each piston's height can be approximately equal to the half ofits length which provides minimum variation of the clearance between thetop of the piston and contour of the stator circular wall. For instance,with stator inner diameter 4″ (˜100 mm) the length of the piston can be2.13″ (54 mm) and the height-0.9,″ (23 mm) and the variation of the gapbetween the top part of the of the piston (at its apex seal) will be ina range of 0-0.012″ (0-0.3 mm.) This small variation or apex seal normalbreathing can be easily accommodated by its sliding in the seat.

[0067] The “ideal” geometrical configuration will involve pistonsegments of twice less radius than the stator contour wall and with anyconfiguration of the piston assembly it will be always a precise contactbetween the piston's outer circular part and the circular contour wallof the stator. Sealing will be a challenge though with respect to thisconfiguration, however in the high rpm devices the “close to zero” gaptechnique can be employed where depending on the density of workingfluid very sufficient pressures can be achieved without seals at all,but with minimum clearance between parts. This particular configurationwill be preferable with ceramic, composite or plastic parts employedwhich can be especially advantageous for “lubricant free” engines aswell as in “micro” engines etched from the silicone based materials,etc.

[0068] In its preferable configuration the apex and side seals aresimilar to the Wankel type seals with the advantage of having much morefavorable leaning angle of apex seals (not more than 10 degrees comparedto between 16 to 30 degrees for Wankel type engines.)

[0069] The geometry of other variations and details of engines andcycling volume machines is described in the diagrams enclosed herein.The variations of shapes of the “oval” stator or geometry of the camsurfaces and other parameters are numerous and can be analyzed usingstandard math analysis techniques. The geometry chosen will determinethe compression ratio and displacement of the engine. The shape of thecurve always has to conform with two points: #1 and #2 (see FIG. 36),the distance between them has to be equal to the side of the square3(c), and a polar angle (gamma) between them must be equal 90 degrees.Such curve has an indefinite amount of solutions (shapes) predeterminedby the ratio a/b and by at least one fragment of the curve betweenpoints 4 or 5 and 6 which are the reference points for all possiblecurves with similar ratio “a/b”. However, points 5 still remain commonreference points for all possible curves.

[0070] Compression ratio of present engine is not limited by itsgeometry, contrary to the Wankel type engines where it cannot exceed15.5:1 (for three lobes rotor.) Displacement of engines as per presentinvention has to be compared to eight cylinder four cycle engine, as itwill have equal number of power strokes per one shaft revolution. As anexample, the circular stator shape engine as per present invention withdisplacement 2.7 liters will have diameter of the contour wall ofapproximately 12″ and thickness of 3.3″ only.

[0071] The central shaft can be linked with at least two oppositepistons in a way described in a prior art, i.e. by a coupling arm or twoarms. However, as the angle between arms changes during the rotationthis method will prove difficult to implement in terms of equaldistribution of the torque from all four pistons. Another disadvantageof such solution will be an alternative difficulty of rotating the shaftduring the starting procedure due to possibility of cam rolls gettingstuck when approaching lean angles with the cam surface, especially incase of engines or compressors with higher compression ratios.

[0072] As per preferable embodiment the central shaft has a cross-likeshape with four slots engaging with corresponding axes of theparallelogram links at their crossings. Thus, either the torque can betransferred to the output shaft alone, or both: the torque and thelateral force resulting from the internal chambers' pressure can betransferred through the pistons depending on the configuration chosen.

[0073] While the cam mechanism itself can withstand these lateral forcesand provide creation or the torque, it is more advantageous to separatethese two functions as it is shown in the preferred embodiments. Severalmeans as illustrated can be employed for such configuration includingpivoted arms, rolls, etc. This solution will also provide betterdynamical response to the pulsating loads received during the powercycles and improve torque creation and transmission system.

[0074] Because the duration of peak pressure at the top dead center ismuch shorter than in the conventional piston or Wankel type engines, theshape of the combustion chamber is much less critical. It can be assumedhowever that the least total surface area of the combustion chamber willbe desired in order to improve thermal efficiency of the engine. Twospark or glow plugs can be employed similar to the approach used inWankel type engine in order to improve combustion.

[0075] Intake and exhaust ports can be located in the side covers or inthe stator or rotor, or in both. In order to simplify the design,laminated structure for the stator or rotor or both can be employed.Intake and exhaust ports can then be provided in a form of slots orbunched openings provided in the plates (lamellas) which, after puttingthem together and tightening or sintering, will provide internalchannels as well as any desirable outer or inner shape configuration.

[0076] Distribution of the wear and heat will be expected to be quitesimilar to the Wankel type engine with more sealing capabilities for theapex seals due to the lower lean angles of the seals.

[0077] The engine with “oval” stator configuration can be provided withdifferent types of chamber compositions. The preferred embodimentincludes a stator ring with pistons surrounding it from the inner orouter portion of the stator ring. In case of inner position of thepistons it becomes possible to employ a conventional oil pan (oil pool)for lubrication which significantly simplifies the overall design,improves reliability and provides low emissions.

[0078] The number of pistons surrounding stator can vary fromapplication to application with minimum four pistons employed. A “chain”like structure can be achieved with multiple chambers or a “wavy” diskcoupled with a single or multiple tiltable chamber/s. This configurationcan be effectively used in pumps, pneumatic brakes for vehicles (a pumpwith closed output and “wavy disk” like stator), propulsors for watercrafts etc.

[0079] In case of water craft engines, the parts can be made of polymerplastic/composite and the whole engine can be submerged into the waterfor effective cooling. Each piston can have a blade attached for it fordirect propulsion. The same configuration can be used for airplanes orducked fan engines.

[0080] Continuous seals are also described herein in combination withtoroidal stator or toroidal shape rotor pistons. These seals are as higheffective as conventional piston engine seals. In addition, the “onepiece” molded, extruded or etched rotor assembly with flexible seals isshown.

[0081] In the instance of four stroke combustion engines, the fourchambers can be used in a close circuit and the cycles are defined asfollows: intake-compression-expansion-exhaust. Ports for intake canutilize a conventional carburetor or can be fitted with gas or dieselfuel injector. Alternatively, the fuel can be injected directly into thechamber. Also a continuous combustion can be achieved by utilizing aflame pilot technique or providing a channel between chambers.Alternatively, the compression diesel igniter can be used as perpreferred embodiment where the pressure of air/fuel mixture ismechanically multiplied by differential piston as per diagrams below.

[0082] Effective ignition timing advance can be achieved by usingelectronic ignition or controlling the injection of fuel directly intothe combustion chamber. A spark plug cavity can be exposed to the innervolume of the combustion chamber by means of porting by rotating pistonsthemselves.

[0083] The engine as per preferred embodiment does not require a flywheel as the inertial capability of the four piston assembly issufficient for providing smooth rotation even on low rpms. Projectedhighest rpm of the engine is about 3000-5000 rpm due to four firings perrevolution which in many cases will require less complicated gear box orno gear box at all.

[0084] Cooling of the engine can be done by air, water or oil in atraditional for rotary (particularly Wankel type) engines way. In caseof employment of oil pan the intensive circulation of the oil utilizingan external heat exchanger for cooling and filter can be provided. Innervariable volume of the engine also can be used for pumping the coolingagent or fuel mixture into the engine. Alternatively, the cooling and/orlubricating systems can employ simply a mixture of the oil with fuel aswell as more complex distribution systems. One of the systems include anintake port opening connected with carburetor through the inner volumeof the rotor which can provide effective cooling of the links andpistons by the intake air and/or fuel. The inner volume can be furnishedwith valve/s for providing pumping/vacuum capabilities to it.

[0085] The engine as per present design can work as an expansion typemachine with numerous types of fluids like steam, compressed/liquifiedgases, hydrogen and solid fuel burners, etc.

[0086] As further illustrated in FIGS. 165, 166, two cycling machines asper present invention can be arranged in a such way that one machinewill compress oxidizer (air, for instance) and deliver it along withfuel into a high pressure combustion chamber where the products ofcombustion will be fed into expansion machine as per present inventionand part of the energy created can be fed back to the compressor. Thesimilar configuration of external combustion engine can employ a hybridsystem where the compressor can be driven by electric motor, etc. it isimportant to note that practical devices described and provided hereinare for illustrative purposes only and should not limit the scope andintentions of present invention.

I claim:
 1. A rotary cycling machine able to produce mechanical energyfrom pressurized fluids as well as to pump, vacuum and compress fluids,and comprising: a cylindrical hollow housing having an internal contourwall and having two plane side covers parallel to each other andperpendicular to the housing central axis; an assembly of four linkedpistons protruding between said side covers and articulating one to theother about parallel axes at the ends of the pistons and where oppositepistons remain parallel to each other during this articulation; theassembly of said four articulating pistons rotating inside said housingcontour wall about said central axis and where said four axes of thepiston assembly have cycling trajectory orbiting said central axis; saidpistons carrying seating means between them, apex sealing means betweeneach of them and said contour wall and a system of lateral sealing meansin conjunction with them and said plane side covers; four chambers ofvariable cycling volume, each defined by the internal contour wall, twoside covers and the adjacent parts of each piston with said sealingmeans between them positioned within said volume; a set of ports in thesaid housing or side covers or pistons for either intake, exhaust,lubrication or cooling or any combination of such; wherein the shape ofassembly of said articulating pistons during one revolution is changingfrom lozenge to square and back to lozenge at least once and; whereinthe outer radial shape of each piston when the assembly of pistons is inlozenge configuration is generally conforming the shape of the internalcontour wall so that the said chamber between two adjacent pistons hasminimum volume and is defined in a desirable way, and when the saidassembly of pistons is arranged in a square configuration the mid apexpart of each piston has the least distance to said contour wail and saidchamber between two adjacent pistons reaches its maximum volume.
 2. Acycling machine as defined in claim 1 where said articulating piston hasshape of a segment with outer curved portion facing said contour wall.3. A cycling machine as defined in claim 1 where said sealing meanscomprise at least one of the following: single or multiple plates orcurved strips, flexible members, rolls, spring loaded sliding gate typeseals or tight tolerance small gaps between the adjacent moving orrotating parts.
 4. A cycling machine as defined in claim 1 wherein saidassembly of articulating pistons comprises a single piece with flexuralpivots and sealing means and is preferably made by methods of extrusionor etching.
 5. A cycling machine as defined in claim 1 wherein the saidhousing contour wall is generally shaped like a circle.
 6. A cyclingmachine as defined in claim 1 wherein the said housing contour wall canbe deformed in its radial direction providing equal number of areas ofmaximum curvature and intermediate areas of minimum curvature.
 7. Acycling machine as defined in claim 1, wherein each piston has more thanone apex sealing means spaced apart along the outer radial portion ofthe piston and facing the contour wall.
 8. A cycling machine as definedin claim 1, further comprising: at least one pair of two parallel toeach other and pivotally interconnected with each other at theirintersections rods with pivots at their free ends connected to said fourpistons; a central shaft coaxial with said central axis and having acoupling mechanism with said piston assembly comprising a radial memberpreferably connected to at least one pivoting intersection of said rodsby traction slot in a such manner so that the radial cycling movement ofthe pivoting crossings of the rods remains possible; at least one cammechanism providing at least one maximum and at least one minimumdistance between its surface and the said central axis, connected to atleast one of said side covers and having at least one roll rockingagainst the said cam surface and connected to any portion of saidassembly of articulating pistons or said rods at the point which has anoscillating orbit against said central axis and preferably through thepivoting intersection of said rods.
 9. A cycling machine as defined inclaim 1 wherein the cycling inner volume defined between saidarticulating pistons and said side covers is used for creation of anadditional flow of fluid for cooling, mixing, lubrication, fluidre-distribution or other purposes or combination of such.
 10. A rotarycycling machine able to produce mechanical energy from pressurizedfluids as well as to pump, vacuum and compress, and comprising: acylindrical housing having a contour wall with two plane sides parallelto each other and perpendicular to the housing central axis; an assemblyof at least four pivotally linked with each other beds with side coverssurrounding said two plane sides of the contour wall and articulatingone to the other about parallel axes at their ends; the assembly of saidarticulating beds with side covers rotating inside or around of saidcontour wail about said central axis and where said axes of the assemblyof said linked beds have cycling trajectory orbiting said central axis;said beds with covers carrying seating means between them and thecontour wall with plane sides, namely sealing means between each of themat the ends of the beds and said contour wall and a system of lateralsealing means in conjunction with side covers of the beds and said planesides of the contour wall; number of chambers of variable cycling volumeequal to the number of said beds, each defined by the contour wall, beditself and its two side covers; a set of ports in either said contourwall, its plane sides, or side covers of the beds or any combination ofthese used for intake, exhaust, lubrication or cooling purposes;
 11. Acycling machine as defined in claim 10 wherein said contour wall has asemi-toroidal shape geometrically merged with plane side covers.
 12. Acycling machine as defined in claim 10 wherein said seals comprises onecontinuous seal per one bed.
 13. A cycling machine as defined in claim10 where said sealing means comprise at least one of the following:single or multiple plates or curved strips, flexible members, springloaded sliding gate type seals or high tolerance small gaps between theadjacent moving or rotating parts.
 14. A cycling machine as defined inclaim 10 wherein said assembly of articulating pistons is composed froma single piece with flexural pivots and sealing means and preferably ismade by method of extrusion or etching.
 15. A cycling machine as definedin claim 10, wherein the said housing contour wall is generally ovallike shaped with at least two minimum and at least two maximumcurvatures.
 16. A cycling machine as defined in claim 10, furthercomprising: at least one pair of two parallel to each other andpivotally interconnected with each other at their intersections rodswith pivots at their free ends connected to at least four of said bedsor their side covers; a central shaft coaxial with said central axis andhaving a coupling mechanism with said assembly of beds or their sidecovers comprising a radial member preferably connected to the pivotingintersections of said rods by traction slots in a such manner so thatthe radial movement of the pivoting intersections of the rods remainspossible. at least one cam mechanism providing at least one maximum andat least one minimum distance between its surface and the said centralaxis, connected or being part of said contour wall or its plane sidesand having at least one roll rocking against the said cam surface andpreferably connected to the pivoting intersection of said rods or to anyother point of articulating assembly of beds or their side covers whichhave a cycling orbit against said central axis.
 17. A cycling machine asdefined in claim 10 wherein the cycling or rotating movement ofarticulated beds or their side covers is used for splashing of lubricantor cooling agent from the pool.
 18. A cycling machine or propulsor asdefined in claim 1 or claim 10 where said exhaust ports have jet nozzlesfor acceleration and direction of the exhaust gases in order to createthrust.
 19. A cycling machine as defined in claim 18 where said portsare opened with delay related to the moment of reaching by said variablevolume chamber its minimum volume.
 20. A cycling machine as per claim 1or claim 10 where said contour wall and said ports are defined by edgesof layers of plates combined with each other in a stack.
 21. An externalcombustion engine comprising at least one compressor utilizing rotatingarticulated pistons or beds assembly with shaft and providing supply ofcompressed oxidizer or fuel or their mixture to the high pressurecombustion chamber with exhaust for products of combustion.
 22. Anexternal combustion engine as defined in claim 21 where said exhaustconnected directly or through heat insulated passage to the expansionmachine utilizing articulated pistons or beds assembly.
 23. An externalcombustion engine as defined in claim 22 where at least some mechanicalenergy produced by expansion machine is transferred back to saidcompressor shaft and the remaining part is used for a power output. 24.An external combustion engine as defined in claim 22 where saidexpansion machine is mounted directly in the vehicle wheel or other typeof propulsor.
 25. An external combustion engine as defined in claim 21where said combustion chamber is similar to ones employed in turbojet orrocket engines capable of withstanding high internal pressures andtemperatures.
 26. An internal combustion engine as per claims 1 or 10where each of said minimum volume variable chambers comprises at leastone ignition device.
 27. An engine defined in claim 26 where saidignition device comprises a cylinder with differential piston having thefirst end with greater square area exposed to the inner volume of saidchambers and connected to a second end with lesser square areacompressing the gas drawn from said chamber to a higher pressure andrising its temperature above the temperature of ignition.
 28. A cyclingmachine as per claim 1 or claim 10 where said contour wall is ofvariable shape.
 29. A rotary engine as per claim 1 or claim 10 wheresaid housing has oil pan.